Winding machine



S. L. ABBOTT WINDING MACHINE May 28, 1963 Filed April 11, 1957 States limits This invention relates to traveling spindle winding machines of the type in which the traveling winding units include yarn traversing means, the machine including a non-traveling drive roll along which the winding units travel, and the winding unit including a tire for driving the traversing means from the drive roll. Machines of this type are disclosed in United States Patent No. 2,135,485.

Because a traverse cam requires a certain diameter and the outside diameter of the tire needs to be larger than the diameter of the cam, this previous construction imposed a limit upon the maximum average speed of the traverse cam for any given roll speed. This limit upon the cam speed imposed a limit upon the sharpness with which the traverse cam follower could be reversed at the ends of the cam and upon the sharpness with which the course of the yarn could be reversed by the traversing thread guide in forming the two ends of the winding package.

A principal object of the invention is to impart to the traverse cam a higher speed of rotation than that of the tire which drives this cam.

In the accompanying drawings,

FIG. 1 is a view in the nature of a plan of a head of a traveling winding unit and a portion of the package drive roll, but with parts removed and broken away to expose the yarn traversing means of the winding unit;

FIG. 2 is a sectional view showing the connection between the package drive roll and traverse cam shaft;

FIG. 3 is a right side view of the device of FIG. 2; and

FIG. 4 is a diagram illustrating the substitution of a tire of the same thickness but larger in internal and external diameter, compared to the tire of FIGS. 2 and 3, for the purpose of providing a higher speed ratio between package drive roll and traverse cam.

As in usual traveling spindle winders the head includes a box-like casing carrying a bracket 11 which is connected by a drag link 12 to a traveling chain 13. Wheels 14 and 15 support the head upon the upper flange of a rail 16. Wheels 17 and 18 are at a level to engage the outer face of rail 16. An arm- 20 pivoted to bracket 11 carries a roll 21 engaging the inner face of rail 16 and a spring 23 reacts on the head and upon a link 24 connected to arm 20, so as to pull the head in toward the rail. Wheel 17 at the left of the unit is thus held against rail 16. Wheel 18 does not engage the rail 16 at the portions of the course of travel at which the package drive rolls are present, because at the right side of the head a tire 25 carried by the head bears against the package drive roll 26, being held in firm driven engagement therewith by the force of the spring 23.

A grooved traverse cam rotates in bearings 31 in the ends of casing 10 and operates a cam follower 33 to reciprocate a thread guide slider 34 upon a rod 35. The cam 30 is preferably formed of nylon so as to be light and have much less inertia than a metal cam, thereby to respond quickly to changes in driving speed. The slider has a notch 34a in which the winding yarn is carried.

The traverse cam shaft 30a, upon which the traverse cam is fast, extends out the right side of the head shown in FIG. 1 and carries the driving structure of the present atet invention and which is shown in greater detail in subsequent figures of the drawings.

Whereas with former tire constructions the traverse cam has been driven at the same angular velocity as the tire, the present tire drives the traverse cam at a greater angular velocity than that of the tire, thus permitting a desirable increase of traverse cam speed relative to the speed of the drive roll 26 and the winding package. The traverse of the winding yarn can thus be reversed more sharply at the ends of the winding package than with former tire constructions.

Referring to FIG. 2 the traverse cam shaft 30a carries a cylindrical pulley comprising for example a sleeve 50, a slightly flaring disk 51 and a slightly flaring cap 52. Preferably there is tightly secured to the surface of sleeve 50 a further sleeve 53 of cork or other material affording a good friction drive surface. A set screw 55- in the end of shaft 301: detachably holds the pulley parts against a collar 56 which is fast on shaft 30a.

An annular tire 25a of cork or similar material is interposed between the package drive roll 26 and the pulley. The radius a of the tire engaging the pulley is greater than the radius b of the pulley so engaged, as shown by a comparison of the distances a and b in FIG. 2. Thus the pulley and traverse cam are driven at a/ b times the speed of the speed of the tire.

Where the roll 26 has a diameter of 2 inches and the tire 25a has a diameter of 3 inches the tire will rotate at /3 the speed of the roll. When a/ b is as in FIGS. 2 and 3 the speed of the traverse cam shaft will then be %X 7 relative to the speed of the package drive roll, i.e., the same as the speed of the package drive roll. Since as shown in FIG. 1 the diameters of the drive roll 26 and cam 30 are the same, then, since the speed of rotation is the same for the drive roll and cam, the surface speeds of the drive roll and cam will be the same. The construction of the prior patent, referred to above, in practice provided a cam speed lower than that of the drive roll.

Due to the increased speed of the cam drum of the present device relative to the speed of winding, its slider can make its reversals at the ends of its strokes more quickly, with reference to the speed of winding, than in the machine of the prior patent, thereby improving the formation of the end faces of the package.

It will be seen that the surface speed of drive roll 26 directly determines the surface speed of the packages and of the outside diameter of the tire 25a, that the surface speed of the inside diameter of the tire is less than that of the outside diameter by the ratio of inside to outside diameter which is 1% :3 or %:1 but that the pulley member is so small inch diameter) as. compared to the 2 inch diameter cam 30 that the surface speed of the cam will, in the absence of slippage, be equal to that of the outside diameter of the tire, the drive roll and package.

When the surface speed of the cam thus equals the surface speed of the outside diameter of the tire, the ratio of pulley diameter to cam diameter necessarily equal-s the ratio of tire inside diameter to tire outside diameter. In the device of FIGS. 2 and 3 these ratios are each 0.3751 and of course are the same when radii instead of diameters are compared.

By removing the cap 52 the tire can be removed for substitution of a different tire.

The diagram of FIG. 4 shows how the ratio of speed of traverse cam to speed of package drive roll can be increased by simple substitution of a tire whose external and internal diameter are each /2 inch larger than those of the tire of FIGS. 2 and 3. In FIG. 4 the tire will rotate at time-s the speed of the roll 26. The ratio a/ b is now and the traverse cam will rotate at the speed of roll 26, that is, approximately the speed of roll 26.

The ratio of pulley diameter to cam diameter remains the same as in the device of FIGS. 2 and 3 having a 3 inch tire, namely 0.375 :1, but this ratio is now less than the ratio of tire inside diameter to tire outside diameter, namely 1% :3 /2 or 0.46411.

In FIG. 3 may be seen a small bracket 60 extending from the end face of the winding machine head. It may be explained that this bracket extends beneath the tire and near enough to the tire to prevent the tire from spinning in an orbital path around the pulley when in reaching the end of the machine the tire is free from the drive roll.

I claim:

A traveling spindle winding machine of the type in which a winding unit including quick traversing yarn-traversing means, which includes a rotatable drum, travels along a non-traveling package-drive roll, the winding unit including a tire for driving the traversing means from the non-traveling drive roll, characterized by a pulley interposed between an inner diameter portion of the tire and the drum, said inner diameter portion of the tire having a greater effective radius than that of the pulley, the ratio between the efiective radius of the pulley and the radius of the rotatable drum of the traversing means being substantially as small as or smaller than the ratio between the eifective inside and outside radii of the tire,

and the surface speed of the drum being substantially as great as or greater than the surface speed of the drive roll.

References Cited in the file of this patent UNITED STATES PATENTS 

